Machine tool



y 6, 1943- EYE. KELLEY 2,323,663

MACHINE TOOL Filed Nov. 6, 1940 r 3 Sheets-Sheet l.

Filed Nov; 6, 1940 July 6, 1943. I; E. KELLEY MACHINE TOOL v Fil edNoIv. 6, v1940 5 Sheets-Sheet 3 Patented July 6, 1943 UNITED STATES PATENT OFFICE MACHINE. TOOL Elmer Elsworth Kelley, Hartford, Conn.

Application November 6, 1940, Serial No. 364,533

7 Claims.

This invention relates to machine tools.

It has among its objects to provide an improved machine tool of the so-called two-at-atime type wherein a plurality of work pieces in different spindles are operated upon simultaneously by like tools, and, more particularly, to provide such a machine embodying improved mechanism whereby the range of use of a machine of this type is materially extended. A further object of this invention is to provide improved plural speed driving mechanism for such a machine whereby the spindles thereof may be operated simultaneously at different selected speeds in the cycle of operation, in such manvner as to enable the machine to meet Wholly new conditions. Still other objects of this invention are to provide improved mechanism for controlling the spindle speeds in such manner as to coordinate the operation thereof with the operation of the other mechanisms of the machine, and to provide improved change speed gearing and clutch mechanism controlling the connection thereof whereby, while obtaining these results, it is also made possible to provide an exceedingly simple, rugged and longwearing structure for the purposes set forth. These and other objects and advantages of this invention will, however, hereinafter more fully appear.

In the accompanying drawings there has been shown for purposes of illustration one embodi- ,ment which this invention may assume in pracbeing shown in plan to facilitate illustration;

Fig, 4 is a sectional View on line 4-4 of Figure 3; Fig. Fig.

a section on line -5 of Figure 4;

5 is 6 1s a detail section on line 6-6 of Fig- Fig. '7 is a sectional View on line 1-1 of Figure 1, and

Fig, 8 is a sectional view on line 8-8 of Figure'l, the mechanism to the left of that line being shown in elevation.

In this illustrative construction, a tWo-at-atime machine has been shown of the general type described and claimed in Patent No. 2,201,182, Kelley, while illustrating in connection therewith an improved form of plural speed spindle drive and improved controlling mechanism therefor of the general type described in Patent No. 2,270,310 of Elmer E. Kelley, and heretofore only capable of being provided in a machine of the so-called standard type illustrated in that patent, wherein the work in different spindles is alternately operated upon by like tools.

Herein, as usual in two-at-a-time machines, the machine includes a plurality of work rotating spindles I rotatable by a central rotatable shaft 2 extending longitudinally between the axes of the spindles and carrying longitudinally spaced low and high speed pinions 3 and 4, respectively, which constantly mesh respectively with pairs of cooperating gears 5 and 6 on the spindles l; improved automatically operating clutch controlling mechanism generally indicated at 1, herein being provided between the shaft 2 and the spindles l which carry usual associated work gripping and feeding mechanism, all as hereinafter more fully described.

Referring more particularly to the mechanism 1, it will be noted that the same controls the operation of the spindles I through controlling the driving effect of the gears 3 and 4, More specifically, the gear 3 is herein provided with an overrunning clutch between the hub 8 of the same and the tooth carrying portion 9 thereof (Fig. 6) usual spring pressed rollers 8a movable in suitable wedge slots in the hub being adapted to grip or release the tooth carrying portion 9 of the gear. As shown, the rollers 8a are adapted to grip the portion 9 and accordingly drive the gear 3 from the shaft 2 when the hub 8 is rotated in a clockwise direction, as shown in Figure 6, while the balls 80. release the portion 9 for overtravel of the latter relative to the hub 8 when the tooth carrying portion 9 is rotated at a higher speed than the hub 8 in the same direction by the gears 5, as hereinafter described.

Herein also the speed of rotation of the toothed portion 9 of the gear 3, and therefore the driving effect of that gear, is controlled by the mechanism l which also controls the connection of the high speed gear 4 to the shaft 2. As shown, this mechanism 7 includes a shipper I0 mounted on suitable oppositely located splines or keys II on the shaft 2 and carrying one-half l2 of a toothed clutch, having twelve equally spaced teeth thereon adapted to engage with a toothed half 13 having three teeth thereon and suitably nism therefor.

fixed to the gear 4; the teeth on both portions l2 and I3 having their engaging faces disposed at such angles as to permit ready disengagement at high speed. Herein the gear 4 is attached by keying the hub I 4 of the portion [3 to the gear, While both the member [3 and an inner bearing sleeve 15 are maintained in longitudinal positioln by a collar [6 pinned to the shaft at IT. Thus, whenever the shipper i9 is in the position shown in Figure 5, the gear 4 is driven from the shaft 2 through the cooperating toothed clutch portions l2 and I3, while the gear 3 is rotated at such a speed by the gears 5 as to make its tooth portion 9 overrun the hub portion 8 and accordingly render it ineffective as a driving gear. When, however, the shipper I is moved longitudinally along the shaft 2 to disconnect the toothed clutch portions l2 and I3, thej high speed gear 4 is therebyautomatically disconnected from the shaft 2 and ceases to drive the gears 6, while the gears are then driven at low speed from the gear 3 which, being of smaller diameter, produces a low speed drive of the spindles l.

Cooperating with this improved high and low speed gearing is improved controlling mecha- Herein, a shipping lever 18, suitably pivoted at I9 on the frame, has a lower forked end disposed in a usual annular groove 20 in the shipper l0 and an upstanding arm 2| on the opposite side of its pivot. Herein, this arm 2i also carries a beveled cam block 22 on its upper end, and improved cam means are provided for engaging this block and thereby swinging the lever l8 about its pivot H) in such manner as to disconnect the clutch elements I2 and I3 at the proper time in the operation of the machine, while a spring 22a coiled about the pivot 29 constantly acts to maintain the elements it and IS in connected relation. As shown, a cam shaft 23 disposed parallel to and above the shaft 2 has a suitable collar 24 fixed thereon which is, in turn, provided with an annular flange 25. This flange, in turn, carries cam members 2G suitably angularly adjustable relative thereto, herein, for example, by screws 21 in an .annular V groove 21a on one face of the disc. Herein, these members 26 have beveled cam portions 28 thereon which are radially disposed and spaced from one another by 180 and adapted alternately to engage the correspondingly beveled block 22. Thus, when one cam member 26 engages block 22, the arm 2| and shipping lever 18 are operated to retract the shipper l0 and ac cordingly release the gear 4 in such manner as to enable the spindles I then to be driven from the shaft 2 through gears 3 and 5, the parts being held in this relation by the engagement of one of the cam portions 28 with the block 22 and the elements l2, l3 being automatically returned into engagement by the spring 22a as soon as the member 26 passes off of the block 22. When the other cam 26, being oppositely disposed, comes around, it will similarly strike the block 22 and similarly actuate the parts 2i, l8 and the shipper ill in such manner as again to interrupt driving through the gear 4 and its cooperating gears 6, the parts thereafter again being automatically returned to their high speed gearing connecting position by the spring 22a as heretofore described.

In my present construction, the cam shaft 23 is a part of the operating mechanism for the a-time machines.

as usual from the low speed sleeve 29 coaxial with the shaft 2, and, in turn, drives a pinion 3U meshing with a gear 3| on the shaft 23, while the latter shaft also carries the usual vertical tool slide operating cam 32 which operates through well known mechanism including a transverse cam slide 32a and usual vertical cutoff tool slides 33 carrying cut-off tools 34. Here, it will also be noted that this mechanism includes a separate V type cam for each vertical tool slide 33 and that these cam mechanisms are, as usual, so operated that each slide 33 moves through two complete cycles of operation for each revolution of the cam 32. Moreover, the pinion 33 meshes with a lower gear 35 on the cam shaft 3: operating the horizontal tool slide, a usual cam 37 being carried on the front end of this shaft and cooperating in a usual way with the transverse cross slide 38 carrying forming tools 39, this shaft 36 being the same shaft which drives the usual feeding and gripping mechanism, generally indicated at 40.

Thus, it will be evident that as the shaft 23, which carries the cam 32, is rotated through each half of a revolution, the shipper Ill will be automatically controlled in such manner as normally to maintain a high speed drive from the gear 4 during the major portion of each cycle of operation of the machine, only interrupting the high speed drive from the gear 4 and establishin a low speed drive from the gear 3 when one or the other of the cams 26 engages the block 22. Further, it will be apparent that through the successive engagements of the cams 26 with the block 22, the shipper will be positively operated in clutch opening direction, while both the transverse tool slide 38 and the vertical tool slides 33 will be operated in such manner that their respective tools 39 and 34 will engage the work during the high speed portion of the cycle of operation.

Operatively associated with the mechanism above described is also the longitudinal tool carrier 41 carrying suitable parallel, longitudinally disposed tools, herein indicated at 42, which are cutting during the slow speed portion of the operating cycle. This longitudinal tool carrier 4i is operated in a usual manner in such machines from a drum cam 43 disposed around the axis of the shafts 2 and 29 and keyed to the latter, this cam acting upon a suitable cam follower 44 carried on the carrier 4! in such manner as to effect the usual forward and back movemerits of the carrier 4| during each cycle of the machine. Herein, the tools 42 are in the form of usual trip type die heads adapted for cutting external threads, but it will be understoodthat any other suitable tools may be substituted therefor, as, for example, tapping, reaming, drilling or other tools which may require a slow rotation of the work spindles during their cutting operation. Further, it will be understood that a usual stock stop mechanism 45 is suitably adjustable about the axis of the shafts 2 and29 and is carried on and rotatable with an outer sleeve 46; this stock stop mechanism comprising oppositely directed arms carrying usual stock stops 4'! adapted to engage the stock simultaneously fed through both spindles l by the stock feeding and gripping mechanism 40, while these stock stops 4! and the arm 45 are adapted to be swung into their stock stopping position and out of the same, in such manner as to permit the use of the tools 42, by suitable cam mechanism generally indicated at 48 and operated from a '53 in any usual manner.

usual internal cam (not shown) on the main cam I-Iere, also, it will be understood that the die chasers of die heads 42 have usual operating members 49 and 50 operated respectively by cams and trips 52 carried on a fixed part of the machine and adapted to engage and operate the members 49 and 50 of f the die heads as the latter are moved longitudinally with the tool carrier 4| relative to the work stock 53.

In the operation of the complete machine, it will be apparent that while the half I2 of the toothed clutch engages the cooperating half [3, the drive to the spindles I will be a high speed drive through the gear 4, and it will be understood that this high speed drive is utilized during these cutting operations which are capable of being performed while the spindles are rotating at high speed, namely those involving the tools 39 and 3G. Further, it will be apparent that the cutting operation of the die heads 42, which requires a low speed operation of the spindles, will occur during the low speed portion of the cycle. Thus, the desired sequence of operation of the several tool slides will coincide with spindle speeds especially adapted to the most efficient operations of their cutting tools, as the work pieces are simultaneously formed and cut oil" on the stock in the two spindles i.

As a result of this improved construction, it is made possible very materially to increase the production obtainable upon a two-at-a-time machine, through the speeding up of certain of the mechanisms thereof during the high speed portion of the operating cycle. Further, by thus adapting the speed of operation of the mechanisms to the particular cutting operations, it is also made possible to increase materially the tool life of the several cutting tools, thereby further increasing the possible production of the machine in a given time. Attention is also directed to the fact that this improved mechanism is of a type which is readily adapted to be embodied in the usual two-at-a-tirne machine with a minimum of change, the high and low speed gearing and its associated controlling mechanism being of a character adapted to be added to such existing machines with a minimum of expense while being closed in the usual gear housing. Further, it will be apparent that through suitable adjustment of the controlling cams, the relative length of the high and low speed portions of the cycle and the relative timing thereof may be varied, as desired, to meet particular conditions, by merely substituting cams of different length or by adjusting the same into the desired angular relation to one another on the rotating cam carrying flange 25. For example, the slow speed drive of the spindles can be limited to the actual cutting time of the longitudinally fed tools, or, if desired, may be extended to include all or a portion of the cutting time of the external forming tool on the cross tool slide. These and other advantages of this improved construction will, however, be apparent to those skilled in the art.

While this invention has been described as applied to one embodiment of the invention, it will be understood that this embodiment has been selected for purposes of illustration, and that the invention may be modified and embodied in other form without departing from its spirit or the scope of the appended claims.

What is claimed as new and desired to be secured by Letters Patent is:

1. In a machine tool having work rotating and feeding mechanism including a pair of work spindles, high and low speed drive means for said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, and controlling clutch means controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, said high and low speed drive means including a common drive shaft extending between said spindles and intermeshing high and low speed drive gears on said drive shaft and both of said spindles, and said controlling clutch means being coaxial with said shaft.

2. In a machine tool having work rotating and feeding mechanism including a pair of work spindles, high and low speed drive means for said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, and controlling clutch means controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, said high and low speed drive means including a common drive shaft extending between said spindles and intermeshing high and low speed drive gears on said drive shaft and both of said spindles, and said controlling clutch means and overrunning clutch means being coaxial with said shaft.

3. In a machine tool having Work rotating and feeding mechanism including a pair of vwork spindles, high and low speed drive means for said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, and controlling clutch means controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, said high and low speed drive means including a common drive shaft extending between said spindles and intermeshing high and low speed drive gears on said drive shaft and both of said spindles and high and low speed drive gears coaxial with said shaft, and said controlling clutch means being coaxial with said shaft and disposed thereon between said gears.

4. In a machine tool having work rotating and feeding mechanism including a pair of work spi dles, a driv shaft common to said spindles, hig and low speed drive means for said spindles including high and low speed drive gears on said shaft and intermeshing high and low speed gears on both of said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means on said drive shaft controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, controlling clutch means on said drive shaft controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, tool feeding mechanism having tools operative on work carried in said spindles, and means controlled by said last mentioned mechanism for automatically controlling the connection and disconnection of said controlling clutch means.

5. In a machine tool having work rotating and feeding mechanism including a pair of work spindles, a drive shaft common to both spindles, high and low speed drive means for said spindles including high and low speed drive gears on said shaft and intermeshing high and low speed gears on both of said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means on said drive shaft controlling the connection of said low speed drive means and having cooperating driving elements overruning whe the spindles are rotated at high speed to disconnect said low speed drive means, controlling clutch means on said drive shaft controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, tool feeding mechanism having tools operative at different cutting speeds on work carried in said spindles, and means controlled by said feeding mechanism for connect- A ing said controlling clutch means while the tools operative at high speed are in use and disconnecting the same when the tools operative at low cutting speed are in use.

6. In a machine tool having work rotating and feeding mechanism including a pair of work spindles, a drive shaft common to both spindles, high and low speed drive means for said spindles including high and low speed drive gears on said shaft and intermeshing high and low speed gears on both of said spindles, and mechanism for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means on said drive shaft controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, controlling clutch means on said drive shaft controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, tool feeding mechanism having a transversely movable tool carrying slide and a longitudinally movable tool carrying slide, and means controlled by said tool feeding mechanism and controlling said controlling clutch for connecting the latter during operation of the tools on said transversely movable slide and disconnecting said controlling clutch means during operation'of the tools on said longitudinal slide.

'7. In a machine tool having work rotating and feeding mechanism including a pair of work spindles, high and low speed drive means for said spindles including a common drive shaft and high and low speed drive gears on said shaft and both of said spindles, and mechanism located between said spindles for selectively connecting said spindles for simultaneous rotation by said high or low speed drive means having clutch means controlling the connection of said low speed drive means and having cooperating driving elements overrunning when the spindles are rotated at high speed to disconnect said low speed drive means, and controlling clutch means controlling the connection of said high speed drive means and the overrunning of said first mentioned clutch means, said controlling clutch including clutch members connectible and disconnectible at high speed and said overrunning clutch means being coaxially disposed with one of the elements of said drive means and having mutuallly engaging elements rotatable together at low speed and relatively rotatable when the spindles are driven at high speed.

ELMER ELSWORTH KELLEY. 

